Bearing



F. l.. 0.- WADSWOHTH.

BEARING.

APPLICATION FILED IuNE I, Isls.

` Patented June i3, 1922.

6 SHEETS-SHEET l.

WIM/Mak F. L. ojwAnsvvoIIIH.

Patented June 13, 1922.

6 SHEETS-SHEET 2.

@r1/vento@ F. L. O. WADSWORTH.

BEARING. APPLICATION FILED LUNE l, 1918,

'Patented June 13, 1922.

6 SHEETS-SHEET 3.

F, I.. Oi WADSWORTH.

BEARING.

APPLICATION FILED JUNI: I, |918,

Patented June 13, 1922.

GSHEETS-SHEET 4.

F. L. o. WADSWORTH.

BEARING.

APPLICATION FILED JUNE 1, 1918.`

Patented June 13, 1922.

6 SHEETS-SHEET 5.

fa@ Ma F. L. 0. WADSWORTH.

' BEARING.

APPLICATION FILED JUNE l. 1918.

Patented June 13, 1922.A

e SHEETS-SHEET ermee.

EBANN I.. o. WADswoBTH, oE PITTSBURGH, PENNSYLVANIA, 'AssIeNoB To' ALBERT BINGSBUBY, oE PITTSBURGH, PENNSYLVANIA.

BEARING.

Specification of Letters Patent. Patented June 13, 1922@ Application'led June 1, 1918. Serial N0. '237,739.

To all lwhom t ma/ z/ concern:

Be it known that I, FRANK L. O. WADs- WORTH, a citizen of the United States of America, and a resident of Pittsburgh,

county of Allegheny, and State of Pennsylvania, United States of America, have invented certain new and useful Improvements in Bearings, of which the following is a specification, reference being hadV to the accompanying, drawings, forming y a part thereof. My invention relates to bearings and particularly to thrust bearings, and has special reference to such as inc ude a mov-1 able or floating bearing member comprising an annular series of double facedy bearing segments or shoes interposed between a pair of. relatively rotatable cooperating thrust supporting or other bearing members.

Floating bearingA members of this character are shown in British Patent No.

875/05 to Michell and in U. S. Patent No.v

as such and practically becomes a partv of` one of the members of the bearing. Moreover, in order that these bearings shall operate to advantage the segments or shoes must assume a slightly tilted position in operation and thereby establish and maintain auto# matic lubrication at the bearing surfaces in accordance with the principles of the'Kingsbury bearings. It is evident however, that if the segments lor shoes are directly interposed between the bearing surfaces the tendency of the thrust pressure on both sides of the same is such as to oppose the tilting of the segments or shoes and if the floating member sticks at one surface thelsegments on shoes are virtually mounted on a Aflat surface with no oil lm interposed, and it is not possible for them to tilt.

According to my present invention I over'- come these objections and difficulties and provide a floating bearing member which is simple'in construction and reliable in operation, by" positively rotating the floating element at a predetermined speed and improv lng 'the structure in various other ways as hereinafterv pointed out. By thus` rotating the floating bearing member, oil films are formed at both surfaces of the floating memher and the segments or shoes are accordingly free t o tilt to the requisite degree and toy maintain the automatic lubrication obtained in the Kingsbury'bearings.

An o bject of my invention is to provide a bearing, `comprising relatively movable bearingmembers, with an interposed floatlng bearingmemberand means operated by the relative movement of said 'members for positively driving said floating element. I

Another object of my invention is to provide a bearing of the character indicated that will start with small friction and operate with an.k oil film continuously maintained between eaoh'ofthe bearing surfaces of the fioating element and the bearing surface with which it cooperates. 1

` Another object of my invention is to provide a simple and inexpensive means for driving a floating element at the desired speed without introducing undue friction or complexity into the bearing.

Another object of my invention is to provide rolling means for temporarilysupport'- ing the load and reducing the friction at starting and also for positively and continuously driving the floating element while the bearing is in operation.

A further object of my invention is to automatically equalize the pressure on the segments or shoes of which the fioating ele. ment is comprised and effect an equitable distribution of pressure on all parts of both bearing surfaces of the shoes individually.

Another object of my invention is to provide for the automatic distribution and circulation of oil in response to the rotation of the floating bearingelement.

Other objects and advantages of my invention will be set forth hereinafter, and in order that my invention may be thoroughly understood I will now proceed to `descrbe the same in the following specification and then point out the novel features thereof in appended claims. The invention is capable of receiving a variety of mechanical expressions, several of which are shown on the ac. companying drawings, but it is to be -eX- sol pressly understood that the drawings are for purposes of illustration only and are not to be construed as definitions of the limits of the invention, reference being had to the appended claims for that purpose.

Referring to the drawings:

Figure 1 is asectional elevation, taken on the line 1-1 of Figure 2, of a thrust bearing arranged and constructed in accordance with my invention and constituting an embodiment thereof.

Figure 2 is a plan View of the same bearing with the rotatable member broken away so that the shaft appears in section.

,Figure 3 is an elevation developed into a single plane, showing the two part, double faced bearing segments or shoes which the floating member of the structure comprises.

The shoe cage which is broken away and shown in section in Figure 3 is shown inl elevation in Figure 4.

Figure 5 is a sectional elevation which corresponds to a small portion of Figure 1 but which illustrates a modified shoe cage and4 rolling bearing structure.

Figure 6 is a partial plan view of the arrangement shown in Figure 5.

Flgure 7 is a sectional elevation on the line 7-7 of Figure 8 and shows another embodiment of my invention in which one piece bearing shoes or segments are employed.

Figure 8 is a sectional plan view on the line 8-8 of Figure 7.

Figure 9 is a developed circumferential section of the floating member showing a portion of the shoe cage and illustrating the vpositions assumed by the shoes when the bearing is in operation.

Figure 10 corresponds to Figure 9 but shows constructionf in which the opposite faces of each shoe are offset circumferentially. with respect to each other.

Figures 11 and 12 are respectively a partial plan view and a sectional detail view of another embodiment, in which the shoe cage has radial members extending substantially through the shoe centers.

Figure 13 is a longitudinal section of a horizontal thrust bearing constituting an embodiment of my invention.

Figure 14 is a transverse section of the same bearing taken on the line 14`14 of Figure 13.

Figure 15 is a diagrammatic section taken on the line 15-15 of Figure 14 and developed into a single.plane.

Figure 16 is a view corresponding to Figure 15`but showing a slightly modified floating ring structure.

Figures 17 and 18 are detail views showing a two-part bearing shoe which may be substituted for the shoes shown in Figure 16.

Figuresl 19, 20 and 21 are views, corresponding respectively to Figures 13, 14 and 1 5, of another horizontal bearing structure which constitutes an embodiment of my invention, Figure 20 being taken on the line 20-20 of Figure 19, and Figure 21 on the lines 21-21v of Figure 20.

Figure 22 is a detail plan view of an oil deflector.

Figure 23 shows another floating ring structure which may take the. place of that shown in Figure 21. f

Figure 24 shows a slight modification of the structure shown in Figure 23.

Figure 25 isa longitudinal sectional elevation of another horizontal bearing structure in which the floating element is positively driven.

Figure 26 is a partial same, looking in an axial direction.

Figure 27 is a plan view showing a portion of the same structure including the oil impellers and deflectors.

Figure 28 is a sectional elevation of a verelevation of the tical shaft bearing having a positively driven floating element.I

Figure 29 is a -partial plan view of the Same. l

Figure 30 is a sectional elevation on the line 30-30 of lFigure 31, showing a modified v `shown in Figure 33 which is a sectional elevation corresponding approximately to Figure 30. Y y

Figure 34 is a sectional plan view of the floating element of the bearing of Figure 33.

Referring first to Figures 1 to 4 inclusive, the form here shown comprises a base 10` having an opening which may constitute .a guide bearing 11 through which aV shaft 12 extends. a thrust block 13 affixed to the shaft, a thrust collar 14 which is suitably secured to the thrust block as by bolts 15, a base ring 16, an equalizing ring 17 mounted thereon, and a floating bearing member 18 interposed between the thrust collar and the equalizing ring.

The baise ring 16 in the form shown has a I an apertured are disposed. The arrangement of parts is such that the floating bearingmember 18, including the bearing rollers 39, andthe cooperating bearing surfaces of the collar 14 and the equalizing ring 17, as well as the spherical surfaces 19 and 20 of the ball and socket joint, are immersed in oil, so that abundant lubrication is insured. The spherical surface 19 of the base. ring is preferably provided with radial oil passages in orderl to permit the oil to flow into the space 26 and supply those portions of the bearing surfaces which are near the shaft, after it has been thrown outward by the centrifugal action due to the rotation of the thrust collar and to the rotation of the floating bearing member 18 at approximately one-half speed.

ln the form shown in Figs. 1 to 4, the floating bearing member 18 comprises a shoe cage 27 comprising" an inner ring 28 provided with an outwardly extending web 29, outer ring 30, and radial webs 31 connecting the rings. The cage is thus subdivided into a plurality of sector-shaped spaces in which two-part, double-faced bearing shoes are disposed. Each of the shoes, as shown in Figure 1, comprises a bottom sector 32, having a bearing surface 33 which cooperates with the bearing surface of the equalizing rings 17 and a top inclined surface 37, and a top sector 35 having a cylindrical projection 36 which engages the inclined surface 37 of the bottom sector and a bearing surface which cooperates with the bearing surface ofthe thrust collar 14. The surface 37 is inclined downwardly toward the shaft in such manner that when the top sector 35 moves radially outward relatively to the bottom sector in response to centrifugal action, the two sectors are wedged apart. This arrangement thus constitutes a simple and effective means for equitably distributingthe pressure upon the several shoes although the bearing surfaces may be irregular and the shoes of unequal thickness due to inaccurate machining or to the frictional heating of the parts in operation.

Each bottom sector 32 is rovided with a spherical projection 38, as shown in Figure 3, which engages the inner surface of the cage ring 30 and prevents outward movement of said bottom sector, but does not inv terfere with the tiltingof the shoe in response to the wedging action of the oil as hereinbefore explained.

lt is evident that there is a component of the thrust pressure which tends to move the sectors 35 inwardly onl account of the 'inclination of the surface 37. This tendency is opposed by centrifugal force due to the rotat1on .of the floating member 18, and the relation between these forces is determined by the speed at which the. floating member rotates and theinclination of the surface 37 I prefer to positively drive the floating member at substantially one-half the speed lof the shaft and thrust collar, and this may be accomplished by means of a plurality of rollers 39, which are mounted on slidable pins 40 in apertures 41 in the outer cage ring 30 and engage both the stationary ring 17 and the rotatable` collar 14. The rollers are slightly tapered, or frusto-concal in form,

hardened steel in order to prevent excessive l wear when the bearing is starting and stopping, and when, as hereinafter explained, the bearing thrust is preferably borne on the rollers alone. Under these conditions the rollers constitute a temporaryl substitute for the bearing shoes and enable the bearing to start and stop with very small friction before the oil filmvhas been established at the surfaces of the shoes and after it has been interrupted.

'The rollersif relied uponvto support ythe thrust pressure for continuous operation, would wear very rapidly, but this is avoided by automatically transferring the thrust to the shoes when the speed reaches a prede- Vtermlined value. When this speed is attained centrifugal force acts on the rollerstending to throw them out in opposition to the springs 42, and thus relieve them from supporting the thrust pressure, but without interrupting their driving contact with the inclined surfaces 43, 44-and also acts on the shoes tending to move the upper sectors 35 outwardly and lift the thrust collar.

Furthermore, the thrust collar is slightly lifted when the bearing shoes assume a tilted position due to the wedging action of the oil. These forces are of course absent when the bearing is not in operation and in stopping the thrust pressure is again supported by the rollers, which are pressed inwardly by the springs 42.

The cylindrical projection 36 extends tangentially relatively to the shaft and permits the sectors 32 and 35 to tilt relatively to veach other in a radial direction, thus insuring an equalization of pressure on all parts of the shoe surfaces although the surfaces of the thrust collar and the equalizing ring may be crowned or distorted by reason of the heating of the parts in operation, or thrown out of parallelism for any cause.

As far as the automatic lubrication of the bearing isconcerned the shoes each act like a one-piece double-faced shoe and tilt circumferentially to establish an oil film at each surface in the manner illustrated in Figure 9.

Briefly the operation of the bearing is as follows: ,When the bearing is at rest the springs 42 hold the. bearing rollers 39 in position to take the thrust and the top sectors of the shoes are free and may be resting against the inner cage ring 28. The bottom sectors are freefrom load and it is obvious that the shoes are particularly free to assume tilted positions when rotative movement is imparted to the floating member.

Assuming that the shaft and attached parts are rotated, the bearing rollers on which the thrust load is now supported are rotated on the pins and `roll on the rim of the egualizing ring 17 with the result that the floating member is revolved about the center of the shaft as an axis at approximately one-half thel speed of the shaft.

The lubricating oil ilmis also immediately established at both bearing surfaces of the floating member. When the rotatin elements have picked up sufficient spec centrifugal force due to the rotation of the floating member causes the sectors 35 to ride up the inclined surfaces 37 and gradually assume the thrust pressure as the speed increases. At the same time the rollers gradually move outward and are relieved of the thrust, but the pressure of the springs 42 is suicient' to continue to hold them in driving contact with the surfaces 43 and 44.

The operation is reversed when the bearing is slowed down, the thrust being transferred to the rollers and the shoe sectors relieved as the centrifugal force diminishes.

Any suitable rolling bearing means may be employed instead of the rollers 39 and a modification of the floating bearing member in which bearing balls are employed is shown in Figures 5 and 6. The collar 14 and the equalizing ring 17 have hardened rims 47, 48 which are substituted for the rims 45, 46 and are provided with curved surfaces 49 to cooperate with bearing balls 5() on the floating member. The cage mayV comprise a ring 51 which is provided with curved notches 52 to hold the balls 50 loosely in place, and spacing rollers 53 may be rotatably mounted on pins 54 between the balls. The balls are pressed inwardly by a resilient band or ring 55. This arrangement corresponds in operation to that of the previous figures.

Referring to Figures 7 to 12 I have here shown another embodiment of my invention in which the shoes 57 are formed of a single piece and are mounted in a cage 58 to which the bearing rollers 59 are attached. Mounted on the base 10 is a ring 60 having a guide ange 61 forming a recess into which a relatively iexiblel bearing ring 62 is set. A plurality of helical springs 63 support the ring 62 and are mounted loosel in suitable recesses 64 in the lring 60.`

loosely fitting dowel pin 65 prevents rotation .of the ring 62.

surface of the ring 62 and comprises the double-faced shoes or segments 57 and the cage 58. In the form shown, the shoes have circumferential grooves 67 and 68 to cooperate with the inner and outerrings 69 and 70 of the shoe cage, and these rings are joined by radial webs 71 which fit loosely into curved grooves 72 in the radial edges of the shoes. The faces of the shoes may be opposite as shown in Figure 9, or offset circumferentially relatively to each other as shown in Figure 10.

The bearing rollers 59 in the arrangement illustrated are mounted on studs 73 which extend through the outer ring 70 of the cage and are screwed into the radial webs 71, thus serving to fasten the parts of the cage together as well as to su port the rollers. The rollers taper inwardly to a slight degree and are pressed in the same direction by'springs 75. The rotating member of the bearing is shown as provided with an oil deflecting flange 74 and the oil circulation-which is dependent upon the centrifugal action .of the parts in operation-is maintained from the spaces around the cooling coils 77, through oil passages 76 in the base ring 60 and into the space near the sleeve 22, from which it is supplied to the bearing surfaces.

By making the faces offset as shown in Figure 10 the thrust pressures have a tendency to tilt the shoes slightly and so facilitate the formation of the oil wedges when the rotatable member of the bearing moves in the direction of the arrow. This arrangement is therefore best adapted for use where the bearing always moves in one direction. The arrangement shown in Figure 9 is well adapted for bearings which are likelyto operate in either direction;

Each of the rollers instead of being pressed inwardly by .a helical spring 75 may be acted upon by a flat spring 80 whichas shown in Figures 11 and 12-is pivotally connected at one end to the cage ring by a link 81 and at its opposite end is adjustably attached thereto by a bolt 82.

As shown in Fig. 12 the radial webs 71a of the shoe cage, instead of extending between shoes as in that of Figures 7 and 8, may be substantially cylindrical and extend through suitable radial holes in the centers ofV the shoes and constitute pivot pins on which the shoes tilt in forming the Kingsbury automatic oil film. l

The structure Shown in Figures 1 'to 12 inclusive are particularly adapted for verti# cal shafts and other thrust bearings where the full load is borne by the bearing at starting and where the starting friction is particularly objectionable.`

In case the bearingV is to be applied to a horizontal shaft where the load is very small at 'starting and -increases with the increase of speed as in the case of `a propeller shaft, it is not necessary to introduce rolling bearings for taking the thrust at any time and under these conditions driving rollers may be employed merely for the purpose of insuring that the floating member rotates at an intermediate speed.

In Figures 13, 14 and 15, I have shown my invention as applied to a horizontal thrust bearing, the structurebeing otherwise similar to the vertical thrust .bearing of Figures 7 and 8 and like parts being designated by the same reference characters. In the form shown, the bearing housing 85 has a journal bearing 86 forthe horizontal shaft 87 and an oil reservoir 88 which is connected to the housing section 91, in which the thrust bearing members are disposed, by a passage 89.

'The thrust block 13 is preferably provided with a substantially radial oil throwing surface 92 to which oil is supplied from passage 89, and a thrust bearing surface 93 with which the floating bearing member co operates.

The housing member 91 constitutes a support on which the relatively stationary member 62 of the bearing is resiliently mounted on springs 63.

The housing extends adjacent to the oil throwing surface 92 of the thrust block and forms a narrow annular passage 94 through which the oil is centrifugally forced by the rotation of the thrust block when the bearing is in operation. The oil then flows radially inward between the bearing surfaces and around the bearing shoes in ac# cordance with the principles of the Kingsbury oil distributing system shown and described in his Reissued Patent No. 14,878, granted J une 8,1920. The circulation of the oil may also be aided by turbiney projections 95 which extend outwardly from the shoe cage between the driving rollers 59 and are formed so as to direct the oil inward as the floating element of the bearing rotates.

The housing member 91 is provided with passages 96 and 97 which establish communication from the space within the floating bearing member adjacent` to the shaft 87 to the reservoir 88 from which it is again supplied through passage 89 to the oil throwing surface 92.

The floating element is driven as in the structures already described and the thrust pressure on the shoes is substantially equalized by the resilient mounting of the ring 62.

The shoes may have their faces oHset as shown in' Figure 15, or directly opposite as shown in Figure 16. In the arrangement of Figure 15 the shoes have their edges beveled at 100 and provided with notches 101 and the shoe cage has radial webs 102 whichare inclined relatively to the bearing surfaces of the shoes so that they fit loosely between the beveled surfaces 100. They are also preferably provided with flanges 103 which engage in the notches 101 in such manner that, when the bearing is operating, the driving forces, transmitted from the cage to the shoes, assist in establishing the automatic oil hfilm at the surfaces by tending to tilt the shoes in the proper direction.

The arrangement of Figure 15 is intended for bearings which operate in one direction only and the arrangement of Figure 16 is preferably used where the bearing is designed to'4 operate in either direction. In this structure the shoe cage has radial webs 104 having flanges 105 which perform the same function as the vflanges 103, one set of -the flanges 105 being operative in either dix rection of bearing operation.

Referring now to Figures 19, 20 and 21, in which like parts are designated by the same reference characters, the ,Hoating ring bearing is composed of a plurality of shoes 115, in the form of ring sectors, flexibly connected at their radial edges by strips 116 of sheet metal. These strips are exible and may be formed of any suitable material. They are secured to the shoes in any suitable manner being, for example, set into grooves 117 as shown in Figure 21 and held in place by rivets 118.

The ring may be constructed by making each shoe in two parts 121 and mounting the parts on opposite sides of a flexible annular connecting member 119, the parts of the shoes being conveniently attached by rivets 120. The partsof the shoes on opposite sides of the flexible member may be directly opposite as shown in Figure 23, or odset as shown in Figure 24, the offset arrangement being preferable if the direction of bearing rotation is always the same.

In the form shown lin Figs. 19 and 20 certain of the shoes 115 are provided with inwardly extending lugs 122 which form bearings for short rotatable shafts or pins A gear wheel 124 is secured to the shaft'87 as shown in Figure 19 and meshes with gear Wheels 125 on the pins 123. A relatively stationary internal gear 126 is affixed to the bearing ring 62 at its inner edge, and meshes with gear wheels 127 on the opposite ends of the pins 123.

The arrangement is such that the rotation of the shaft and attached" gear produces a rotation of the pins 123 and since the'gears 127 mesh with the stationary internal gear 126 a rotation of the floating ring element, including the shoes 115, is the result.

-Attention is directed to the fact that the necessity for a shoe cage is avoided in the constructions shown in Figures 19 to 24, t-he driving gearing cooperating directly with one or more of the shoes which act together by reason of the fiexible connection between them.

The gear ratios are preferably arranged to produce a rotation of the floating rlng bearing member at a speed which 1s approximately a mean between the speeds at whlch the cooperating bearing members rotate. ln the structures illustrated where one of the bearing members is at rest, the floating bearing member will be rotated at half the speed of the shaft 87. It is evident, however, that two or more floating rings may be interposed between the stationary and rotatable members of the bearing and in general the gearing will be such as to equalize the difference in speed between adjacent cooperating members.

1n this arrangement the oiling of the surfaces is effected as before except thatA there are no turbine blades on the floating bearing element and a scraper or deflector 130 is mounted in a recess 131 of the housing and rests on the circumference of the thrust block at the top. It constitutes a means of transferring the oil, which adheres to the'outer surface of the thrust block, to the bearing surfaces.

r1`here are various other ways in which the floating member may be driven and one of them is shown in Figures 25 and 26 to which referencey may now be had. In the form here shown 140 desi ates a thrust member on which an equa izing ring 141 is mounted by a ball and socket joint. The latter has an annular thrust surface 142 which is opposed to a thrust surface 143 on a thrust blocky 144. The thrust block is affixed to a substantially horizontal shaft A floating bearing member is interposed between the thrust surfaces 142 and 143 and comprises a shoe cage in the form of a ring 148 having an inner flange 149 and an outer flange 150 which is provided with propeller vanes 151. Radial lugs p-roject inwardly from the flanges 149 and 150 and divide the cage into spaces in which the shoes f 147 are loosely mounted. The shoes act like the two-part double-faced shoes of Figure 1 except that they are provided with spherical bottom surfaces 152 so that they are free to tilt in all directions.

An internal gear ring 154 is affixed to the base 140 and the inner ring 149 of the cage is provided with gear teeth so that it constitutes an internal gear. A nut 156 holds.

the thrust block 144 against a shoulder of the shaft and constitutes a support for one or more driving pins 157 each of which extends parallel to the'axis'of the shaft and has a pinion 158 in position to mesh with the internal gear 155 and a gear wheel 159 which meshes with the stationary internal gear 154. ln the form shown in Figures 25 and 26 there are two pins 157 and two sets of gears, but any suitable number may be employed. The arrangement is such that when the shaft rotates together with the thrust block 144 and the nut 156, the pins 157 revolve, due-to the fact that the gears 159 mesh with the internal gear 154, and consequently the shoe cage is driven by the pinions 158, the driving speed being approximately one-half the speed of the shaft.

The circumferential surface of thelthrust block serves to carry oil from the bottom of the casing upwardly to the top and I prefer to provide a scraper such as that indicated at 160 to cause the oil to flow downwardly through the bearing surfaces and between the shoes.

The tendency for the oil to flow outwardly due to the rotation of the fioating bearing member is more than oHset by thecentrifugal action of the thrustl block 144 which .rotates at a higher speed and is provided at 163 with propeller ribs which cause the oil to move radially outward and then flowin inward between the shoes in accordance with the principles of the Kingsbury reverse lubrication, to which reference has already been made. The circulation of oil is established from the interior of the floating member axially through passages 164 and downwardly through passages 165 in the base 140, communication being established through an axial passage 167 at the bottom of the housing to an oil. reservoir 168, from which it flowsthrough a passage 169 to the surface 163.

When two setsof shoes are employed and are mounted on opposite sides of the .shoe cage the intermediate web of the latter may be tapered as shown in Figure 28 so that each of the sector 35 of the construction shown in Figure 1. The invention is here shown as adapted to a foot-step bearing and the shoe cage 176 is provided with lugs 170 in which pins 171 are rotatively supported. The gear 172 on one end of each pin meshes with a gear ring 173 on the thrust collar 1735" and the gear wheel 174 on the opposite end of each pin meshes with the stationary internal gear 175.

The cage in this construction has a hub 177 which fits onto the shaft 178 and has internal helical 4oil conveying grooves 179 which distribute the oil between the two sets of shoes. The oil circulation is inward through passage 178a and outward around the bearing shoes and between the' opposed bearing surfaces 173b and 179b of the collar 173a and the base ring 1795.

Referring to Figures 30 to 34 inclusive, the general object of these constructions-as in `all of those previously described--is to shoes acts like the upper provide a positively or semi-positively driven shoe-cage, carrying a number of bearing segments or shoes interposed between the thrust bearin-g surfaces of the stationary` and rotatable members of the bearing and capable of assuming tilted positions withreference' thereto when the parts attain normal speeds of rotation.

A. further object of the structures now under consideration--as in the case`of some of the forms previously shown,-is to provide for an easy start from rest by the utilization of the rollers or balls .which drive the cage as a means for assuming the load when 'the bearing is at rest and during the starting period. These rolling elements arev relieved when thefloating member of the bearing has attained its normal speed by the action of centrifugal force on some radially movable portions or members of thel floating element.

In the previously described constructionsl operating in the aforesaid manner, the balls or rollers are moved outwardly in opposition to springs and are thusrelieved from the load although they still maintain a driv ing contact with `the race ways with which they cooperate, and one or more of the sectors of a two--part shoe may move radially under the influence of centrifugalforce t0` aid in the performance of this function.

1n the structures under discussion, this object is attained by fixing the balls or rollers against any radial movement with respect to their race ways and lifting or separating the race ways when the oating member is rotating at normal speed by the radial movement of the segmental bearing elements or shoes vunder the infiuence of centrifugal force.

1n the arrangement of Figures 30, 31 and 32 the thrust collar 180 has a beveled bearing surface v181 and is opposed to a relatively stationary flexible bearing ring 182 which is mounted on adjustable studs 188 of the base 184 and has an oppositely beveled annular bearing surface 185. There is interposed between the surfaces 181 and 185 an annular floating element 186 which is tapered or wedge-shaped in cross-section and cooperates with the beveled surfaces of the stationary and rotatable members 'o f the bearing. The parts are so arranged that the surfaces 181 and 185 diverge radially outward from the `center of the shaft.

The floating element comprises a cage composed of an inner ring 187, an outer ring 188 of channel-shaped section, and a plurality of radial studs 189 which are circumferentially distributed and constitute bearings for a plurality of frusto-conical rollers 190 which cooperate with the bearthey are disposed@ When the bearing is at rest and when 191 composed of parts, designated 191 and 1911, which are mounted back to back with rear beveled surfaces 192 co-operating. The bottom part 191b of each shoe'is held against outward movement in a radial direction by engagement of the lug 193 thereon with the cage ring 188'. The inclination of the beveled surfaces 192 is greater than the inclination of the beveled surface 181; consequently the tendency of the thrust pressure exerted by the thrust collar 18() on the upper part 191a of the shoes is to force the upper part radially inward against the cage ring 187.

The parts are so constructed and proportioned that when the top members of the shoes occupy positions as shown at the left in Figure 30, the shoes make a very light Contact with the bearing surfaces 181 and 185, the load being borne by the rollers 190.

/Vhen the bearing is in operation, the

pressure is largely assumed by the shoes and the rollers only maintain driving contact. Thus the rollers are free from excessive wear although the bearing sustains very heavy loads.

r1`he position of the shoes relative to the cage isrmaintained by loosely-fitting dowel pins 194 and the relation between the parts of the shoes is maintained by loosely-fitting dowel pins 195. The inner surface of the inner cage ring 187 is preferably provided with helical grooves 196 which are arranged to transfer oil upwardly, into the space between the sleeve 22 and the bearing member 180, when the bearing is in operation.

The rollers are not necessarily placed between the shoes and since their radial positions are fixed they may be cylindrical or spherical and may cooperate with parallel surfaces as in the arrangement of Figures 83 and 34.

In'the form shown in these figures, the base ring 197 is mounted on the base 198 with a ball and socket joint, the base being provided with a spherically curved surface 199 with which the cooperates. A loosely fitting dowel p1n 200 prevents the rotation of the ring without in-` terfering with its rocking to equalize the thrust pressure on its bearing surface 201. A thrust collar 202 having a beveled bearing surface 203 is mounted on the thrust block 13 within the race ring 204. It is preferably flexible to some extent' and has a crowned supporting surface which permits the bending or flexing of the ring to enable it to cooperate with the-beveled top surfaces of bearing shoes 205 even though one or both of the surfaces may have a tendency toward distortion by the heat generated in .the parts when the bearing is in operation or from some other cause.

The shoes 205 are secured in proper circumferential position in the cage by pins 206 which extend loosely through suitable holes in the shoe sectors and connect the inner and outer rings of the cage which are designated 207 and 208. Similar pins 209 may be disposed between the shoes but they are not necessary unless to strengthen the cage.

The outer cage ring 207 vis provided with a plurality of pockets 210 in which are dis-4 posed bearing balls 211. These balls engage the race surface 212 of the rlng 204 and the opposed race surface 213 on the vbase ring 197.

balls 211. Under normal operating conditions however, the bearing balls engage the race ways sufficiently to drive the floating element at half the speed of the rotatable memberof the bearing, but the centrifugal force exterted on the shoes', is sufficient to compress the springs 214 and wedge the shoes between the opposed bearing surfaces 201 and 203. The thrust pressure is thus taken by the shoes under operating conditions.

Theshoes are particularlyfree to tilt and establish automatic oil films as in the structure of the previous figures.

In the last described constructions the two surfaces of the shoes are not radially adjustable or tiltable with respect to each other and equitable distribution of the bearing pressure on radial lines is secured by the flexing of the base ring 182 of Figures 30 to 32 and of the thrust collar 202 in the structure of Figures 33 and 34.

Provision is made for the circulation of oil under the base ring 182 between the studs 183 and, in the arrangement of Figures 33 and 34, the base ring 198 is provided with grooves 215 for the same purpose.

Structures of preferred form and con struction have been illustrated and described for the purpose of showing ways in which this invention may be used, but the inventive thought upon which this application is based, is broader than these illustraseries of segments or shoes interposed be-l tween the thrust surfaces of the relatively rotatable members, and means for driving the floating menrber at a predetermined speed less than the speed of the rotatable bearing member. f

2. In a thrust bearing, the combination of a pair of relatively rotatable bearing members having opposed thrust surfaces, a floating bearing member comprising a series of segments or shoes interposed between the thrust surfaces of the relatively rotatable members, and means cooperating with the rotatable member of the `bearing for drivin the floating member at substantially oneha f the speed of the rotatable bearing member.

3. In a thrust bearing, the combination of a pair of relatively rotatable bearing memvbers having opposed thrust surfaces, a floating bearing member comprising a series of segments or shoes interposed between the thrust surfaces of the relatively rotatable members, and means cooperating with the rotatable member of the bea-ring for driving the floating member at a predetermined intermediate speed whereby the relative speed between the cooperating parts of the bearing is reduced.

4. In a thrust bearing, the combination of a pair of relatively rotatable bearing members having opposed thrust surfaces, a floating bearing member comprising a series of segments or shoes interposed between the thrust surfaces of therelatively rotatable members, and gearing for establishing a driving connection between the rotatable member of the bearing and the floating member.

5. In a thrust bearing, the combination of a pair of relatively rotatable bearing members having opposed thrust surfaces, a floating bearing member comprising a series of segments or shoes interposed between the thrust surfaces of the relatively rotatable members, and one or more rolling members rotatively mounted on the floating member and held in operative engagement with both members of the bearing, whereby a rotation of the floating member at an intermediate speed is produced.

6. In a thrust bearing, the combination of relatively rotatable bearing members having opposed thrust surfaces, an equalizing support for one of said members, a oating bearing member comprising a series of segments or shoes interposed between the thrust surfaces members, and means for driving the ioating member at a predetermined speed less than the speed of ythe rotatable bearing member.

7. A thrust bearing comprising a relatively stationary bearing member, a rot'atable bearing member, an interposed floating bearing member comprising a series of bearing segments or shoes arranged to tilt radially, and means for driving the floating bearing member at a predetermined speed.

8. In a bearing, the combination of relatively rotatable members, an interposed rotatable surface-bearing member and rolling;l

bearing means for taking the load at starting.

9. In a bearing, the combination of relatively rotatable members, an interposed rotatable surface-bearing member and centrifugally actuated rolling bearing means for taking the load at starting and stopping.

10. In a bearing, the combination of relatively rotatable members, an interposed rotatable surface-bearing member and rolling bearing means for driving the surface bearing member and for taking the load therefrom at starting and stopping.

11. In a thrust bearing, the combination of relatively rotatable thrust members, an-

interposed relatively rotatable surface-bearing member, and means associated with the surface-bearing member for driving the `same at a speed less than that of the rotatable thrust member. A

12. ,In a thrust bearing, tliecombination of relatively rotatable thrust members, an interposed relatively rotatable surface-bearing member, and rolling bearing means engaging the relatively rotatable thrust menibers and'associated with the interposed rotatable surface-bearing member.

' 13. In a thrust bearing, the combination of relatively rotatable thrust members, an interposed relatively rotatable surface-bearing member, and means cooperating with the relatively rotatable thrust members and arranged to drive the interposed rotatable surface-bearing member at an intermediate speed.

14. In a thrust bearing, the combination of relatively rotatable thrust members. an interposed relativelyI rotatable surfacebearing member, and roll-ing bearing means engaging the relatively rotatable thrust members andarranged to drive the inter-v posed rotatable surface-bearing member at an intermediate speed and adapted to take `the load at low speeds.

15. In a bearing, the combination of rela- 4at a predetermined of the relatively rotatable tively rotatable members and an interposed floating bearing member comprising rolling bearings and surface-bearing members adapted to assume thetlirustl load speed.

16. In a bearing, the combination of relatively rotatable members and an interposed floating bearing member comprising rolling bearings and surface-bearing members ependent on centrifugal action for taking thev load when the bearing is in operation.

17. In a bearing the combination of relatively rotatable members and an interposed floating bearing member comprising rolling bearings and surface-bearing members subdivided into radially tiltable sectors.

18. In a bearing, the combination of relatively rotatable members and an interposed floating bearing member comprising rolling bearings and surface-bearing members subdivided into radially tiltable sectors, said sectors being circumferentially tiltable in pairs to establish voil films-at the bearing surfaces.

19. In a bearing, the combination of relatively rotatable members and an interposed floating bearing member comprising rolling bearings and surface-bearing members subdivided into sectors, said sectors being radially movable relative to each other and having cooperating surfaces at least one of which is inclined relatively to the plane of the bearing surfaces.

20. In a bearing, the combination of relatively rotatable members and an interposed floating bearing member comprising surface-bearing sectors and rolling bearing members adapted to be centrifugally re-` lieved of the bearing load when the bearing is in operation.

21. In a bearing, the combination of relativel rotatable members, an interposed floating bearing member comprising surface-bearing sectors and tapered rolling bearing members cooperating with inclined annular surfaces on the relatively rotatable members, and springs for pressing the rolling bearing members into engagement With the inclined surfaces.

22. In a bearing, the combination of relatively rotatable members, an interposed floating bearing member comprising surface-bearing sectorsand rolling bearings cooperating With annular surfaces on the relatively rotatable members, and means for pressingthe rolling bearings into engagement with said annular surfaces.

23. In a bearing, the` combination of relatively rotatable members, an interposed fioating bearing member comprising surface-bearing sectors and tapered rolling bearing members cooperating With inclined annular surfaces on the relatively rotatable members, and springs for pressing the rolling bearing members into engagement`with ativelyy rotatable members, an interposed floating bearing member comprising surface-bearing sectors and rolling bearings cooperating with annular surfaces on the `relatively rotatablemembers, and -means for pressing the rolling bearings into engagement with said annular surfaces in opposition to the centrifugal force resulting from the rotation of the floating member.

25. In a bearing, the combination of relatively rotatable surface-bearing members, an equalizing support for one of said members, an interposed rotatable surface-bearing member and rolling bearingmeans for taking the load at starting.. i

26. In a bearing, the combination of relatively rotatable surface-bearing members, an equalizing support for one of said members, an interposed relatively rotatable surface-bearing member, and rolling bearing means associated with said rotatable surfacebearing member for rotating the same.

27. In a bearing, the combination of rela-` tively rotatable members, anequalizing support for one of said members, and. an interposed floating bearing member comprlsmg rolling bearings and surface-bearing members adapted to assume the load at a predetermined speed.

` 28. Athrust bearing comprising relatively rotatable members, a rotatable segmental ring'bearingmember between the relatively I rotatable members, and means for taking the thrust from the segmental ring bearing member at starting and stopping.

29.'A thrust bearing comprising relatively rotatable members having outwardly diverging rannular bearing surfaces and a yfloating bearing member comprising a plurality of bearing sectors and conical bearing rollers cooperating with the diverging rsurfaces fof said relatively rotatable members.

30. In' a bearing, the combination of relatively rotatable members, asupport for one of said members forming therewith a ball and soc-ketjoint, and an interposed floating 'bearing member comprising rolling bearings and surface-bearing members adapted to assume the thrust load at a predetermined speed.

:bearing members and designed to rotate at a speedless than that of the rotatable bearing member, and. rolling bearing members on said floating member for reducing 1 the starting friction thereof.

32. A bearingcomprising relatively rotatable members, a segmental ring bearing member between the relatively rotatable members,`and means for driving the seg,v

mental ring bearing member at a speed which differs from that of the rotatable member.

33. A vbearing comprising relatively-rotatable members, a segmental ring bearing member between the relatively rotatable members, and meansfor drivingthe segmental ring member at approximately 'onehalf the speed ofthe rotatable member. I

34. A thrust bearing comprising relatively rotatable, members, a rotatable segmental ring bearing member between the yrelatively rotatable members, amd rolling bearing 'member between the rrelatively rotatable members, and means for driving the segmental ring bearing member and for relieving said membery of the thrust at starting. I I

36. A thrust bearing comprising relativelyrotatable`members, a segmental ring bearing member .between the relatively roring bearing tatable members vcomprising, a cage having 'sector-shaped pockets,l and afpairof shoe members 'in each pocket soarranged that a relative radial movementspreadsgthe shoe members.

88. A thrust-,bearing comprising relatively rotatable members, a segmental'ring bearing member between th'e relatively 4rothe radial move-ment of one ofthe shoe members.

39. Al thrust bearing comprising relatively rotatable members, a segmental ring bearing member between the relatively ro- 4tatable members comprising a cage yhaving sectorshaped pockets, a palr of shoe `mem bers in each pocket so arrangedthatv a relative radial movementl spreads the shoemembers, and friction drivingrollers attached to the cage and engaging the rotatable member of the bearing.

tively rotatable members, a segmental 'ring bearing member between the relatively rotatable members comprising a caoe having sector-shaped pockets, a pair of's oe meml 125 40. A thrust bearing comprising relabers in e'achvpocket so4 arranged that a relative radial movement spreads the shoe members, and friction driving rollers attached to the cage and engaging the rotatable member of the bearing, saiddriving rollers for the cage being interposed between the relatively rotatablefbearing membersand adapted to assume the thrust pressure at starting.

41. A thrust bearing comprisingv rela-- tively rotatable members, a segmental ring bearing member between the relatively rotatable members, and bearing rollers also interposed between the relatively rotatable members of the bearing and adapted to be centrifugally adjusted t0 throw the thrust pressureon the segmental ring bearing member at a predetermined speed.

42. A thrust bearing comprising relatively rotatable members, a segmental ring bearing member between the relatively rotatable members, and taper bearing rollers inter-v posed between the relatively rotatable members of ythe bearing and engaging inclined annular surfacesthereon.

43. A thrustbearing comprising relatively rotatable members, a segmental ring bearing member between the relatively rotatable members, bearing rollers having radial axes and inwardly tapered conically curved surfaces interposed between the relatively rotatable members of the bearing and engaging inclined annular surfaces thereon, and springs pressing the rollers inward against the inclined surfaces.

44. A thrust bearing comprising relatively rotatable members having outwardly diverging annular bearing surfaces and an interposed floating surface-bearing member having rolling bearing means and arranged to cooperate with the inclined surfaces of said members.

45. A thrust bearing comprising relatively rotatable members having outwardly diverging annular bearing surfaces and -an interposed loating bearing member arranged to cooperate with the inclined surfaces of said members and havin'g means for driving the floating member at a predetermined speed.

46.. A thrust bearing comprising relatively Irotatable members having outwardly diverging annular bearing surfaces, an interposed floating surface-bearing member comprising a. series of bearing elements of wedge-shape in radial section, and means for driving thesame from the rotatable bearing member at a reduced speed.

' 47. A thrust bearing comprising relatively rotatable members having outwardly diverging annular bearing surfaces and anl inter'- posed floating ,bearing lmember comprising a series of two-part bearing sectors radially adjustable relative tov each other. and arranged to engage the bearing surfaces of the relativelyrotatable members.

48. A thrust bearing comprising relatively 'prising an annular rotatable. members having outwardly diverging annular bearing surfaces and an interposed iloating .bearing member Acomprising a plurality of bearing sectors and driving rollers interposed between said rotatable members.

49. Athrust bearing comprising relatively rotatable members having outwardly diverging annular bearing surfaces and an interf 51. A thrust bearing comprising relatively r rotatable members having diverging frustoconical surfaces opposed to 4eachl other, an interposed bearing member rotatable between said relatively rotatable members and comprising an annular cage having an inner ing annular bearing surfaces and an interring, an outer ring, and a `plurality of radial rods, tapered bearing rollers rotatable 'on said rods, and surface-bearing elements for taking the load from the rollers when the bearing is in operation.

52. A lthrust bearing comprising relatively rotatable members having diverging frustoconical surfaces opposed to each other, an interposed bearing member rotatable between said relatively rotatable members and comcage having an inner ring, an outer ring, and a plurality o'f radial rods, tapered bearing rollers rotatable on said rods, and bearing sectors interposed between said rotatable members.

. 53. A thrust bearing comprising relatively rotatable members having opposed 'annular bearing surfaces at least one of which is frusto-conical., and an interposed annular floating surface-bearing member cooperating with said surfaces.

54. A thrust bearing comprising relatively rotatable members'having opposed annular bearing surfaces at least one of which is frusto-conical, an interposed annular floating bearing member cooperating with said surfaces, and means for driving the interposed lloating member.

55. A thrust bearmg comprising relatively 1254 rotatable members having opposed annular bearing surfaces at least one of which is frusto-comcal, an interposed annular float- 1ng bearing member cooperating w1th sa1d surfaces, and rolling bearing members asso- Mie ciated with the floating element and arranged to drive the same. i

56. In a thrust bearing, the combination of relatively rotatable members having annular bearing surfaces and opposite beveled race surfaces, an interposed rotatable s urface-bearing member having a plurality `of sectors or shoes', and sprin -pressed taper rolls forming parts of the oating bearing member and cooperating with the oppositely beveled race surfaces.

57. In a bearing, the combination of relatively rotatable members having main annular bearing surfaces and one of said members having a frusto-conical race, an interposed rotatable floating surface-bearing' member, androlling bearing members associated therewith and cooperating with the frusto-conical race.

58. ln a bearing, the combination of relatively rotatable members, an interposed oat- Ving bearing member having rolling bearing membersand adapted to cooperate with the movable bearing members, and radially movable bearing shoes adapted to take the thrust from the rolling bearing members.

59. In a bearing, the combination of relatively rotatable bearing members, a floatlng bearing member interposed between s aid bearing members, and means for drivmg said floating bearing member at a speed less than that of said rotatable bearing member. 1 60. In a bearing, the combination of relatively rotatable bearing members, a floatin bearing member interposed between sai 4 bearing members, and rolling bearing members carried by said floating bearing member and engaging said relatively rotatable members for rotating said Vfloating bearing y member. y

6l. In a thrust bearing, the combination of relatively rotatable bearing members, a floating bearing member interposed between ,said bearing members, rolling bearing members carried by said floating bearing member and engaging said relatively rotatable members for rotating said floating bearing member, and means .mounting said rolling bearing members whereby they carry the load of. said bearing when said bearing is at rest but move in response to centrifugal force to relieve the ressurev on 'said rolling bearing members when the bearing is in operation. t

62. ln a.V thrust bearing, the combination of relatively rotatable bearing members, a floating'bearing member interposed between said bearing members and comprising twopart shoes, and rolling bearing members carried by said floating bearing member and engaging said relatively rotatable members for rotatin said floatingmbearingv member, the ,parts o said shoes being relatively movable in response to centrifugal force to relieve the 'pressure yon said rolling bearing members when the bearing is in operation.

the lpressure on said rolling bearing members when the bearing is in operation.

64. lna thrust bearing, the combination of relatively rotatable bearing members, a floating bearing member interposed between said bearing members, radially movable rolling bearing members carried by said floating bearing member and engagingsaid relatively rotatable me'mbersfor rotating said floating bearing member, and means opposing radial movement of said rolling bearing members whereby they sustain the load on said bearing when the ybearing is at rest but move in response to centrifugal force to relieve the pressure onv the rolling bearing members when the bearingis in operation.

65. ln athrust bearing, the combination of relatively rotatable bearing members, a floating bearing member. interposed between said bearingl members and comprising twopart-shoes the parts of which are radially tiltable with respect to each otherand members carried by said floatingbearing members and cooperating with said relatively rotatable members for rotating said -Hoating bearing member.

66. In a thrustbearing, the combination of relatively rotatable bearing members, a floating bearing member interposed between said bearing members and comprising a series ,of bearing Vsegments or shoes, means mounting said segments or shoes whereby they may tilt radially, and members carried by said floating bearing member and cooperating with said relatively rotatable members for rotating said floating bearing member.

67. lln a thrust bearing, the combination of relatively rotatable bearing members, a floating bearing'member interposed between said ybearing members and comprisingv a .series of bearing segments or shoes, and rolling bearing members carried by saidfloating bearing member and engaging said relatively rotatable members for rotating said floating bea-ring member, said .segments or shoesy being mounted to move in' response-to centrifugal force and relieve thepressure on said rolling bearing members-*when the bearin is in operatio y 68. n ya thrust bearing, the oombinationof relatively rotatable bearing members provided with diverging bearing surfaces, a floating surface' bearing member interposed between said bearing members, and frustoconical bearing rollers carried by said floating bearing member and engaging said diverging bearing surfaces for rotating. said floating bearing member.

69. In a thrust bearing, the combination of relatively rotatable bearing members provided with diverging bearing surfaces, a floating bearing member interposed between said bearing members, and frusto-'conical bearing rollers carried by said floating bearing member and engaging said diverging bearing surfaces for rotating said floating bearing member, said rollers being movable in response to centrifugal force to relieve thepressure on said rollers when the bearing is in operation.

70,v In a thrust bearing, the combination of relatively rotatable bearing members, a floating bearing member interposed between said bearing members and comprising a series of bearing segments or shoes, and:

means for rotating the. floating bearing member and sustaining the load on the bearing when the bearing is at rest, said lastnamed means cooperating with said floating bearing member to transfer the load. to said segments or shoes when the bearing is in operation.

71. In a bearing, the'combination of relatively rotatable'bearing members, an interposed rotatable surface-bearing member, and means for driving the surface-bearing member adapted to assume the load at starting and stopping and mounted to be actuated by centrifugal force'to transfer the load to said surface-bearing'member when the bearing is in'operation.

72. In a bearing, the combination of relatively rotatable bearing members, an interposed rotatable surfa'ce-bearing member comprising radially movable bearing segments, and means for driving the surface bearing member, said bearing segments being constructed to transfer the load to said'driving means at starting and stopping and to move radially to assume the load when the bearing is in operation.

73. A bearing comprising relatively rotatable bearing members, an interposed floating bearing member, and means on the floating bearing member for moving the oil into cooperative relationship with the bearing surfaces.

74. A bearing comprising relatively roing re tatable bearing members, an interposed floating bearing member, means for rotating said floating bearing member, and means on the floating bearing member vfor moving the oil into cooperative relationship with the bearing surfaces.

75. A- bearing comprising in combination with a rotatable shaft, an outer non-rotatable casingsurrounding the shaft but spaced therefrom, a rotatable bearing member coolperating with a bearing surface on said s aft,-'and means for automatically revolving said member at a speed less than that of the shaft.

76. In a bearing, the combination of relatively rotatable bearing members, a floating surface-bearing member interposed between said bearing members, means for driving said floating bearing member, and means for mounting said driving means whereby the sameassumes the load at starting and stopping and transfers the load to the surfacebearing ationship with the same bearin is in operation.

77. n a bearing, the combination of relatively rotatable bearing members, a floating bearing member interposed between said bearing members and comprising a plurality when the -of bearing se ments, and means for driving said floating earing member adapted to assume the loadat starting and stopping, said bearing segments being mounted to assume the load while the bearing is in operation without discontinuing the driving relationship of said driving means.

78. In a thrust bearing, the combination of relatively rotatable bearing members, a floating bearing member interposed vbetween said bearing members, and rolling bearing members on said floating member cooperating with inclined surfaces on said relatively rotatable. bearing members to sustain the thrust when the bearing is at rest, said rolling bearing members being movable under the influence of centrifugal force to transfer the thrust to said floating bearing member.

79. In a bearing, the combination of relatively rotatable bearing members, a floating surface-bearing member interposed between said bearing members, and rolling means cooperating with said floating member to drive the same at a predetermined speed.

In witness whereof, I have hereunto set my hand this 29th day of May, 1918.

FRANK L. O. WADSWORTH.

member while maintaining the driv, 

